Ratchet one-way clutch assembly unit with wide biasing springs

ABSTRACT

A ratchet one-way clutch assembly with wide biasing springs. The assembly has an inner race with a plurality of notches, an outer race with a plurality of pockets, and a plurality of pawl members positioned in the pockets for engagement with the notches. Spring members which extend the axial width of the pawl members provide tilting forces on the pawl members toward engagement.

CROSS-REFERENCE TO RELATED APPLICATIONS

This is a continuation-in-part of U.S. patent application Ser. No.08/917,880, filed on Aug. 27, 1997, which in turn is acontinuation-in-part of U.S. patent application Ser. No. 08/707,104,filed on Sep. 3, 1996 now U.S. Pat. No. 5,853,073.

TECHNICAL FIELD

The invention relates to ratchet one-way clutch assemblies withcentrifugally engaging/disengaging pawls.

BACKGROUND ART

There are various types of one-way clutch assemblies in use today. Suchclutch assemblies include sprag-type, roller-type, and pawl ratchet-typeassemblies. All of these one-way clutch assemblies work satisfactorilydepending upon the particular application in which they are used.

In certain transmissions, increased torque capacity is needed forone-way clutch assemblies. Space constraints also require that the sizeof the clutch assembly be retained within certain limits. Currentone-way clutch assemblies with sprags or rollers are often insufficientto add increased load carrying capacity and still maintain the spaceconstraints.

Pawl one-way clutch assemblies can add increased nominal load capacityfor a given package size. The design limits of a ratchet-type pawlclutch assembly are dictated by contact stress between the pawls and theraces and/or bending, shear, and hoop stresses generated within theraces.

Ratchet clutch assemblies have at least one pawl which acts to lock twonotched or pocketed races together in one direction and rotate freely inthe other direction. In general, the differences between known ratchetclutch assemblies relate to the control of the movement of the pawls andthe effect on that movement by centrifugal forces.

Ratchet clutch assemblies are shown, for example, in U.S. Pat. Nos.2,226,247, 3,554,340, and 5,449,057. Another ratchet clutch assembly isshown in British Patent No. 2116. The '340 patent discloses afree-wheeling bicycle hub assembly with a ratchet clutch. Under theaction of centrifugal forces at high speed, the pawls can be thrown outof the joints and suffer extreme wear.

The '247 patent discloses another bicycle free-wheeling hub assemblywith a ratchet clutch assembly. The pawls have a rectangularcross-section and are positioned loosely in the pockets in order to movefreely. The looseness makes the position of the pawl center of mass andthus the movement of the pawl uncontrollable.

In the '057 patent, the motion of the pawls is controlled by pivotingaxles that pass through the pawls. The axles are positioned on aretainer and add complexity and cost to the design. It is also difficultto position the holes in the pawls for the axles with sufficientprecision for high speed operation.

In the British 2116 patent, the pawls are mounted on axles positioned ona retainer. The axles again add complexity and cost to the design. Also,centrifugal loading during high speed operation will create high forceson the axles and could adversely affect the operation of the clutch.

It is an object of the present invention to provide an improved ratchetone-way clutch assembly. It is another object of the present inventionto provide an improved ratchet clutch assembly which has improvedoperation at high speeds.

It is still another object of the present invention to provide a ratchetone-way clutch assembly in which the pawls are provided with a tiltingforce or inclination toward engagement. It is a still further object ofthe present invention to provide a ratchet one-way clutch assembly whichutilizes springs to place tilting forces on the pawls toward engagement.It is an additional object of the present invention to utilize spring orbiasing members which provide biasing forces on the pawl memberssubstantially along the axial widths of the pawl members.

SUMMARY OF THE INVENTION

The present invention provides a ratchet one-way clutch assembly whichincludes a plurality of pawls positioned in pockets in the outer race ofa clutch assembly. A plurality of corresponding notches are positionedon the outer circumference of the inner race to mate with the pawls inlocking engagement during relative rotation of the races in onedirection. In one alternate embodiment of the invention the pawls havepeaks or ridges on one side which mate with pivot ridges or recesses inthe pockets in the outer race. The center of mass of the pawls issituated or positioned such that when the clutch rotates the centrifugalforce on the center of mass causes the pawl to move toward the engagedposition. This is accomplished without an axle or stationary pivot.

The ridge in the outer race pocket is located relative to the center ofmass of the pawls in order to control the engaging force. This isnecessary for high speed durability.

In the preferred embodiment of the invention, biasing member, such asspring members, which extend substantially the axial widths of the pawlmembers are used to provide tilting or biasing forces on the pawlstoward engagement. The spring forces can act on the pawl membersthemselves or in recesses that extend axially along the width of thepawl.

Other embodiments of the invention utilize one or more axial retainmentdevices. These devices include pairs of washers, or plastic retainerswith axial extending flange members. The devices retain the pawlsaxially and also hold the races in axial radial alignment, whileallowing relative rotation. The retainment devices also act as thrustbearings and can retain required lubrication to prevent excessive wearof the pawls.

The present invention ratchet one-way clutch assembly has particular usein vehicle transmissions and can be used in environments where bothraces rotate or where one of the races is fixed. The invention can alsobe used in any mechanism where a positive backstop is desired to preventundesired reverse or backward rotation, such as in an escalatormechanism or the like.

Other features, benefits and advantages of the present invention willbecome apparent from the following description of the invention, whenviewed in accordance with the attached drawings and appended claims.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 illustrates a ratchet one-way clutch assembly in accordance withthe present invention;

FIG. 2 is an enlarged view of a portion of the clutch assembly shown inFIG. 1;

FIGS. 3 and 4 illustrate an alternate embodiment of the presentinvention which utilizes spring members, with FIG. 4 being anelevational view and FIG. 3 being an exploded view thereof;

FIGS. 5 and 6 show partial cross-sectional views of the embodiment shownin FIG. 4, the cross-sectional views being taken along lines 5--5 and6--6, respectively, in FIG. 4 and in the direction of the arrows;

FIG. 7 is an enlarged view of a portion of the clutch assemblyembodiment shown in FIG. 4;

FIGS. 8, 9 and 10 illustrate various embodiments of pawl members for usewith a first spring-type embodiment of the present invention;

FIGS. 11 and 12 illustrate an embodiment of pawl members for use with asecond spring-type embodiment of the present invention;

FIGS. 13 and 14 illustrate a still further embodiment of the presentinvention, with FIG. 14 being an elevational view and FIG. 13 being anexploded view thereof;

FIGS. 15 and 16 show partial cross-sectional views of the clutchassembly shown in FIG. 14, the cross-sectional views being taken alonglines 15--15 and 16--16, respectively, in FIG. 14 and in the directionof the arrows;

FIG. 17 is an enlarged view of a portion of the clutch assemblyembodiment shown in FIG. 14;

FIGS. 18 and 19 depict another ribbon spring embodiment of the presentinvention;

FIGS. 20 and 21 depict a coil spring embodiment in accordance with thepresent invention;

FIGS. 22-27 depict further embodiments of the invention; and

FIGS. 28-33 depict still further embodiments of the invention.

BEST MODE(S) FOR CARRYING OUT THE INVENTION

FIG. 1 schematically illustrates a ratchet one-way clutch assembly 20 inaccordance with the present invention. The assembly 20 includes an innerrace 22, an outer race 24, and a plurality of individual pawl members25. The pawl members 25 are positioned in pockets 26 in the outer racemember. A plurality of notches 28 are positioned in the outercircumference or periphery of the inner race 22.

When the motion of the inner race 22 relative to the outer race member24 is in the clockwise direction in FIG. 1, the inner race rotatesfreely. When the relative motion of the inner race member 22 relative tothe other race member 24 is counter-clockwise, the inner race and outerrace are locked together by one of the pawls 25. In this regard, in FIG.1, the locked pawl is indicated by the reference numeral 25'. The pawl25' transmits force through pocket 26 in the outer race and notch 28 inthe inner race.

In the clutch assembly shown in FIG. 1, ten pockets 26 and ten pawlmembers 25 are shown, together with eleven notches 28 in the inner race22. Although the embodiment shown in FIG. 1 only shows one pawl 25' inengagement, more than one pawl can be engaged at one time if the numberof pawls and notches are both wholly divisible by a common denominatorother than one.

FIG. 2 is an enlarged view of a portion of the clutch assembly shown inFIG. 1. The pawl 25 shown in FIG. 2 is depicted in the free-wheelingposition. In accordance with the present invention, the cross-section ofthe pawl 25 has a peak or pivot ridge 30 formed by the intersection oftwo substantially flat sides 32 and 34. The peak 30 of the cross-sectionforms a pivot ridge with the outer race pocket 26 which is shaped toreceive the pawl. In this regard, the pocket 26 has substantiallystraight sides 36, 37, 38 and 39.

Preferably, in accordance with the present invention, the center of mass(CM) of the pawl 25 is positioned to the left of the pivot ridge 30 asviewed in accordance with FIG. 2. In this manner, as the clutch assembly20 rotates, a centrifugal force (CF) on the center of mass (CM) causesthe pawl 25 to move toward the engaged position, that is, the positionwhere it would be engaged with notch 28 in the inner race 22. The torqueon the pawl 25 is proportional to the tangential distance of the CM awayfrom the ridge 30.

Although the embodiment of the invention shown in FIGS. 1 and 2 shows apawl member with the center of mass positioned, together with the pocketin the outer race, such that the pawl has a tendency to move toward theengaged position, other embodiments can be utilized in accordance withthe present invention. For example, the geometry of the pawl can bechanged to provide a pawl with a disengaging tendency. In this manner,the CM could be positioned to the right of the pivot ridge 30.

The pocket 26 in the outer race also has a peak or recess 40 which mateswith the pivot ridge 30 of the pawl member 25. The peak 40 in the pocketholds the pawl 25 in the proper circumferential location for freemovement in the pocket. This prevents the ends 42 and 43 of the pawlmember 25 from coming in contact with the sides 36 and 39, respectively,of the pocket. If the ends of the pawl were to hit the adjacent areas ofthe outer race pocket, friction could slow the movement of the pawltoward engagement. In accordance with the preferred use of the presentinvention, it is necessary for the pawls to rotate into engagement withthe inner race as quickly as possible.

With the present invention, the ridge on the pawl is precisely locatedrelative to the center of mass of the pawl, regardless of the exactlocation of the pawl with respect to the outer race. This allow precisecontrol of the engaging force, which is preferred for high speedoperation. This is also accomplished with a relatively simple geometrywhich does not include an axle, separate pivot member, or the like.Moreover, the outer race pocket is shaped such that it also has acorresponding peak or recess, which retains the pawl in a preciselocation in the pocket. This location prevents the pawl from contactingthe sides or ends of the pocket as it rotates toward engagement.

Preferably, the pawl members 25 are made of a hardened steel materialand formed by pieces cut from a drawn wire. This allows precise controlof the geometry of the pawl, and also allows precise control of thecenter of mass relative to the peak or pivot ridge 30. In this regard,with the present invention, it is possible to control the center of masswithin a tolerance of 0.001 inches.

Another embodiment of the present invention is shown in FIGS. 3-8. Thisembodiment is referred to generally by the reference numeral 50 in thedrawings. In the one-way ratchet clutch assembly 50, a spring is used toprovide a tilting force on the pawl members toward engagement. A springis particularly needed for pawls which are disengaged centrifugally, aswell as for engaging pawls that must engage when the outer race isstationary. In FIGS. 3-8, the assembly 50 includes an outer race member52, an inner race member 54, a plurality of pawl members 56, and a pairof garter springs 58 and 60. A pair of retainment washers 62 and 64 arealso provided in the embodiment shown in FIG. 3 and are discussedfurther below.

As shown more particularly in FIG. 7, the pawl members 56 are positionedin pockets 66 in the outer race members 52 and are adapted to engagewith notches 68 in the inner race 54. The garter springs 58 and 60, onlyone of which is shown in FIG. 7, are made from a small coil of wire andare commonly available. For the embodiment shown in FIG. 3 whichutilizes two garter springs 58 and 60, pawl member 56 is utilized asshown in FIG. 8. The pawl member 56 has a pair of recesses or sidegrooves 70 and 72. The garter springs 58 and 60 are positioned in thegrooves 70 and 72 when the pawl members are positioned in the outerrace. The remainder of the pawl members 56 have sizes and shapes similarto pawl members 25 described above with respect to FIGS. 1 and 2. Inthis regard, the pawl members have a pivot ridge 74 which mates with apeak or recess 76 in the pocket 66.

The operation of the spring members 58 and 60 is shown with reference tospring 58 and pawl members 56 in FIG. 7. In this regard, when the pawlmembers are in their disengaged position, the garter spring 58 providesa force toward outer race member and thus toward the engaging positionof the pawl member. This spring provides a force F (as shown in FIG. 7)against surface 80 of each of the pawl members. When the pawl members 56are in their engaged positions, that is, mated with notches 68 in theinner race, the spring member 58 is relaxed and does not provide aspring force on the pawl members. This is shown with respect to thecenter pawl member 56 in FIG. 7.

The spring force can also be arranged to act on a single side groove ora center groove of the pawl geometry. This is shown in FIGS. 9 and 10,respectively, where the pawl members are referred to by the referencenumbers 82 and 84. The garter spring is indicated in phantom lines andis referred to by reference numeral 86. If either of the pawlembodiments shown in FIGS. 9 and 10 are utilized with the embodiment ofthe invention shown in FIGS. 3-7, then the position of the ribbon springand the number of ribbon springs provided is adjusted accordingly.

Opening or aperture 81 in the drawings (FIG. 6) provides an access holefor lubrication relative to the transmission or other mechanism in whichthe one-way clutch assembly 50 is utilized. Preferably, several accessholes are provided in the clutch assembly, such as the three openings 81shown in FIG. 14.

The spring force on the pawl members can also be applied in anothermanner. As shown in FIGS. 11 and 12, the pawl member 90 has alongitudinally or axially extending groove 92. A small ribbon spring 94is utilized to provide a spring force (SF) in the direction of arrow 96.The ribbon springs 94 are preferably cut from thin strips of springsteel material and are positioned in the grooves 92 in order to providea force SF toward engagement of the pawl members 90.

The washers 62 and 64 are also known as axial retainment devices ormembers and can be used to improve or enhance the operation of thepresent invention. The members 62 and 64 retain the pawl members axially(longitudinally) in the clutch assemblies. The retainment members alsohold the inner and outer races in axial alignment, while allowing freerelative rotation. Moreover, the axial retainment members act as thrustbearings between the clutch assembly and external parts of the mechanismthat are rotating relative to the clutch assembly and must carry anaxial load through the assembly. Finally, the axial retainment members(washers) 62 and 64 can retain lubrication in the clutch assembly whichis required to prevent excess wear of the pawl members.

The washers 62 and 64 can be connected to the outer race through apress-fit arrangement, staking, welding, or mechanical fastening in anyconventional manner.

An injection molded plastic retainer (retainment) member can also beutilized. Such a member 100 is shown in FIGS. 13-17. In these Figures,the one-way ratchet clutch assembly is referred to generally by thereference numeral 102. Together with the retainer member 100, theassembly 102 includes an outer race member 104, an inner race member106, a plurality of pawl members 108, a garter spring member 110 and asecond retainer member 112.

In this regard, in the embodiment of the invention shown in FIGS. 13-17,the pawl members 108 can be of any of the types shown and describedearlier. In addition, the pawl members 108 are contained in pockets 120in the outer race member and engage notches 122 in the inner racemember, in the same manner described above with reference to the otherFigures.

The retaining member 100 has a plurality of flanges or upstandingarcuate-shaped guide members 118 situated to be positioned within theannular space between the inner and outer races 106 and 104,respectively. The member 100 is a radial bearing retainer for the pawlsand the race members, and also acts as a lube dam for lubrication. Theretainer members 100 and 112 are preferably attached together to retainthe clutch assembly together axially. The retainer members also act asthrust bearings between the assembly and external parts of the mechanismthat are rotating relative to the clutch assembly and carry axial loadsthrough the assembly. The retainer members 100 and 112 can be connectedtogether in any conventional manner, such as a press-fit arrangement,staking, ultrasonic welding, mechanical fastening, or the like.Preferably, the retainer member 100 is made from an injection moldedplastic material, and also preferably has a low friction coefficient sothat it can provide improved bearing performance over regularsteel-on-steel bearings.

Another ribbon spring embodiment in accordance with the presentinvention is shown in FIGS. 18 and 19. In this embodiment, pawl members90' are utilized which are the same as pawl members 90 describedearlier. The members 90' have an axial groove 92'. A ribbon springmember 130 has an annular circular shape and is adapted to fit betweenthe inner and outer race members of the clutch assembly. The member 130is preferably made of spring steel and has a plurality of openings orwindows 132 (only one of which is shown), each with a tab member 134.The pawl members 90' are positioned in the openings 132 and the tabmembers are positioned in the grooves 92'. The ribbon spring member 130through the tab members 134 provides biasing forces on each of the pawlmembers 90' in the clutch assembly toward engagement with the notches onthe inner race member.

In accordance with the spirit and scope of the present invention, thespring mechanism for biasing the pawl members toward engagement with theinner race notches can have a wide variety of forms. Other than garterand ribbon springs described above, other spring members, such as coilsprings, leaf springs, and the like could be utilized. In this regard, acoil spring embodiment is shown in FIGS. 20 and 21. One or more coilsprings 140 are positioned in recesses or bores 142 which connect topockets 144 in the outer race member 146. The coil springs 140 bias thepawl members 148 radially inwardly toward the inner race member.

In the embodiment of the invention shown in FIGS. 22-24, the resilientbiasing members extend across all or substantially all of the width ofthe pawl member. In FIG. 22 (which is related to the embodiment shown inFIGS. 18 and 19), the pawl members 160 have an axial groove 162. Aribbon-type spring member 164 has an annular shape and is adapted to fitbetween the inner and outer race members of the clutch assembly. Themember 164 is preferably made of spring steel and has a plurality ofopenings or windows 166 (only one of which is shown), each with a tabmember 168. The pawl members 160 are positioned in the openings 166 andthe tab members 168 are positioned in the grooves 162. The ribbon springmember 164 through the tab members 168 provides biasing forces on eachof the pawl members 160 in the clutch assembly toward engagement withthe notches on the inner race member.

The spring tab member 168 is wider than the spring tab member 134utilized with the embodiment shown in FIGS. 18 and 19. The wide springmember substantially reduces the rolling mode of rotation of the pawlmember. As a result, the wide spring member prevents rattling of thepawl during the free wheeling mode of operation of the clutch assembly.Not only does the wide spring structure restrain the rolling mode ofrotation, but it enhances fluid damping of the pawl members.

Another embodiment of the invention utilizing a wide spring member isshown in FIGS. 23 and 24. In this embodiment, a wide accordion-type (or"Z-spring") spring member 170 is located radially outwardly of the pawlmember 172. The spring member 170 is positioned in a recess or pocket174 in the outer race member 176 which connects with the pawl pocket178. The spring member 170, which preferably is made from a spring steelor equivalent material, pushes the toe 180 of the pawl member 172 intoengagement with the notches in the inner race member. The width of thespring member 170 restrains the rolling mode of rotation of the pawlmember. Fluid and frictional damping are also obtained with this design. The width of the spring member 170 preferably is substantially thesame as the width of the pawl member, although it can also be slightlygreater if space permits.

Another type of accordion or Z-type spring member 200 which can be usedwith the present invention is shown in FIGS. 25-27. The spring member200 is made from a s ingle piece of spring steel or equivalent materialand is cut and folded in the manner depicted. With spring member 200,the folds 202 are oriented in the tangential (annular) direction(transverse to the axial direction of the clutch) with the folds on theends being positioned adjacent the outer or side surfaces of the clutchrace members.

The spring member 200 is used to bias the pawl member 204 in the outerrace member 206 in a direction toward engagement with the notches in theinner race member. Preferably, the spring member 200 extends the entirewidth, or substantially the entire width, of the pawl member 204.

Another wide spring member 210 is shown in FIGS. 28-31B. This springmember is an individual spring member made of stainless steel (springtemper or high yield) and bent into the shape shown. The spring member210 has an inverted V-shaped portion 212 which fits around a groovedrivet 214, which in turn is secured in ancillary pocket 213 adjacent themain pawl pocket 216 in outer race member 215. The flat flange portion218 of spring member 210 fits under recessed portion 222 of pawl member220 and acts to bias the pawl member into engagement with notches 224 ininner race member 226. The pawl member 220 also has a recessed curvedgroove 228 on one surface.

The wide-type spring members of the types shown in FIGS. 22-31B can beplaced in various locations in clutch assemblies, and can be used onvarious types of ratchet clutches, including conventional ratchetclutches, ratchet clutches with pivot ridges on the pawl members, andplanar ratchet clutches. Further, if desired, separate inner and/orouter race members can be eliminated from the mechanical structure inwhich the clutch-type mechanism is utilized, and the pawl pockets andmating "lock-up" notches can be formed directly in the mating mechanicalstructural parts, such as a rotor or shaft.

While the best modes for carrying out the present invention have beendescribed in detail herein, those familiar with the art to which thisinvention relates will recognize various alternate designs andembodiments for practicing the invention as defined by the followingclaims. All of these embodiments and variations that come within thescope and meaning of the present claims are included within the scope ofthe present invention.

What is claimed is:
 1. A one-way ratchet clutch assembly comprising:anouter race member having a plurality of pockets; an inner race memberhaving a plurality of notches; and a plurality of pawl members, one ofsaid pawl members positioned in each of said pockets; biasing means forbiasing said pawl members towards said engagement with said notches;said biasing means comprising spring members positioned in operativeengagement with each of said pawl members, said spring members havingaxial widths substantially the same as said pawl members; said pawlmembers each having a ridge thereon and said pockets each having acorresponding recess for mating with said ridge; said pawl members eachhaving a center of mass positioned relative to said ridge such that uponrotation of said outer race member, the pawl members are moved towardengagement with said notches in said inner race member.
 2. The one-wayratchet clutch assembly of claim 1 wherein a number of notches areprovided which is different in number than the number of pawl members.3. The one-way ratchet clutch assembly of claim 1 further comprising apair of disc-shaped retention members positioned on opposite sides ofsaid assembly.
 4. The one-way ratchet clutch assembly of claim 3 whereinone of said pair of retention members includes a plurality of guidemembers thereon, said guide members being positioned between said innerand outer races.
 5. The one-way ratchet clutch assembly as set forth inclaim 1 wherein said spring members comprise Z-spring members, saidspring members being positioned in recesses in said outer race members.6. The one-way ratchet clutch assembly as set forth in claim 5 whereinsaid Z-spring members are made from a single piece of folded springsteel material.
 7. The one-way ratchet clutch assembly as set forth inclaim 6 wherein the folds as oriented in a direction transverse to theaxial direction of the clutch assembly.
 8. The one-way ratchet clutchassembly as set forth in claim 6 wherein the folds as oriented in theaxial direction of the clutch assembly.
 9. The one-way ratchet clutchassembly as set forth in claim 1 wherein said spring members have aninverted V-shaped portion and are positioned in ancillary recessesadjacent said pockets.
 10. The one-way ratchet clutch assembly as setforth in claim 9 further comprising rivet members in said ancillaryrecesses, and wherein said V-shaped portions are positioned around saidrivet members.
 11. A one-way ratchet clutch assembly comprising:an outerrace member having a plurality of pockets; an inner race member having aplurality of notches; a plurality of pawl members, one of said pawlmembers being positioned in each of said pockets; said pawl membersbeing retained in said pockets during rotation of one of said racemembers in one direction relative to the other of said race members, andat least one of said pawl members being engaged with one of said notcheswhen said race members are rotated relative to each other in theopposite direction; and means for directing said pawl members towardengagement with said notches; said means for directing said pawl memberscomprising spring members positioned in recesses in said outer racemember and having axial widths substantially the same as said pawlmembers.
 12. The one-way ratchet clutch assembly of claim 11 whereinsaid means for directing said pawl members toward engagement with saidnotches further comprises a ridge member on each of said pawl members, acorresponding mating recess member in each of said pockets, and aconfiguration of each of said pawl members which positions the center ofmass thereof relative to said ridge member such that centrifugal forcecauses the pawl member to move toward the engaged position.
 13. Theone-way ratchet clutch assembly of claim 12 further comprising annulardisc members positioned on opposite sides of said clutch assembly,wherein said disc members assist in axially retaining the pawl membersin said pockets.
 14. The one-way ratchet clutch assembly of claim 13wherein one of said disc members includes a plurality of axial extendingguide members, said guide members positioned between said inner andouter race members.
 15. The one-way ratchet clutch assembly as set forthin claim 11 wherein said spring members comprise Z-spring members, saidspring members being positioned in recesses in said outer race members.16. The one-way ratchet clutch assembly as set forth in claim 15 whereinsaid Z-spring members are made from a single piece of folded springsteel material.
 17. The one-way ratchet clutch assembly as set forth inclaim 16 wherein the folds as oriented in a direction transverse to theaxial direction of the clutch assembly.
 18. The one-way ratchet clutchassembly as set forth in claim 16 wherein the folds as oriented in theaxial direction of the clutch assembly.
 19. The one-way ratchet clutchassembly as set forth in claim 11 wherein said spring members have aninverted V-shaped portion and are positioned in ancillary recessesadjacent said pockets.
 20. The one-way ratchet clutch assembly as setforth in claim, 19 further comprising rivet members in said ancillaryrecesses, and wherein said V-shaped portions are positioned around saidrivet members.
 21. A one-way ratchet clutch assembly comprising:an outerrace member having a plurality of pockets; an inner race member having aplurality of notches; a spring member positioned between said inner andouter race members; and a plurality of pawl members, one of said pawlmembers positioned in each of said pockets; said spring member having aplurality of windows; one of said pawl members positioned in each ofsaid windows; said spring member having a tab member in each of saidwindows, each of said tab members biasing a respective pawl membertoward engagement with said notches in said inner race; said tab membershaving substantially the same axial width of said pawl members.
 22. Aone-way ratchet clutch assembly comprising:an outer race member having aplurality of pockets and a recess in operative communication with eachof said pockets; an inner race member having a plurality of notches; aplurality of pawl members, one of said pawl members positioned in eachof said pockets; a spring member positioned in each of said recesses andbiasing a respective pawl member toward engagement with said notches insaid inner race; said spring member having substantially the same axialwidth of said pawl members.
 23. The assembly of claim wherein saidspring member is an accordion-type spring member.
 24. The assembly ofclaim 23 wherein said accordion-type spring member has a plurality offolds thereon and said spring member is positioned in said clutchassembly such that said folds are positioned tangentially therein. 25.The assembly of claim 22 wherein said spring member is a bent piece ofspring steel material and is held in place in said outer race member bya rivet member.
 26. The assembly of claim 22 further comprising a secondpocket adjacent each of said pawl pockets, and a first portion of saidspring members is positioned in said second pocket.
 27. The assembly ofclaim 26 wherein said spring members are secured in said second pocketby rivet members.
 28. The assembly of claim 22 wherein said pawl membershave a curved recess on one external surface.